Divergent cam expansible chamber device



P M. MORSE July 25, 1967 DIVERGENT CAM EXPANSIBLE CHAMBER DEVICE Filed Dec. 21,

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DIVERGENT CAM EXPANSIBLE CHAMBER DEVICE Filed Dec. 21, 1966 4 Sheets-Sheet 2 Paul M. Morse INVENTOR.

July 25, 1967 MORSE 3,332,613

DIVERGENT CAM EXPANSIBLE CHAMBER DEVICE Filed Dec. 21, 1966 4 Sheets-Sheet :3

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4 Sheets-Shet 4 Paul M Morse INVENTOR.

United States Patent 3,332,613 DIVERGENT CAM EXPANSIBLE CHAMBER DEVICE Paul M. Morse, Carlinville, Ill., assignor 0f thirty-three percent to John E. Morse, Eureka, Calif. Filed Dec. 21, 1966, Ser. No. 603,616 14 Claims. (Cl. 230-437) ABSTRACT OF THE DISCLOSURE A fluid compartment separated into radially inner and outer chambers by circumferentially spaced vanes rotataJbly mounted on crankpins for synchronized movement to successively expand and contract the chambers. Valve elements driven with the crankpins control the supply of fluid to the outer chamber and exhaust of fluid from the inner chamber. Fluid is transferred from the outer to the inner chamber at the beginning of each cycle through the vanes which overlap in sliding engagement with each other.

Background of the invention This invention relates to cyclically operative, expansible chamber devices in which fluids are compressed and expanded. The basic structural arrangement and operational principles associated with the present invention are applicable to devices such as fluid motors, pumps, meters as well as internal combustion engines, wherein liquids and/ or gases are being handled.

More particularly, the present invention relates to expansible chamber devices of a type such as disclosed in my prior Patent No. 3,207,425, issued Sept. 21, 1965. In this type of exansi-ble chamber device, a plurality of circumferentially spaced vane members in engagement with each other are rotatably mounted about eccentric axes which are rotated in synchronized relation to each other producing rotation of the vane members themselves about their own eccentric axes by virtue 'of the interengagement between the vane members. The vane members enclose a radially inner chamber that is cyclically expanded and contracted at the same time that a radially outer chamber enclosed by the housing is cyclically contracted and expanded. By appropriately controlling the supply and exhaust of fluid to and from the inner and outer chambers, the expansible chamber device may be utilized as a pump, motor or as an internal combustion engine. In such prior art types of expansible chamber devices, the vane members engage each other at substantially small contact areas approaching point contact in order to reduce frictional losses and wear. Thus, the pressure of the fluid capable of being sealed within the radially inner chamber is limited as Well as the stresses capable of being sustained by the movable parts.

Summary of the invention In accordance with the present invention, an expansible chamber device of the aforementioned type is provided wherein the vane members associated with the device slidingly engage each other over a substantial surface area not only to constrain movement of the vane members as in the case of the prior art but to also more effectively seal the radially inner chamber within which relatively high pressures are developed. Also, as a result of an overlapping arrangement of the vane members, a chamber wall is formed which may better withstand the stresses otherwise developed in prior art arrangements.

An important object of the present invention therefore is to provide an expansible chamber device having a plurality of overlapping vanes that engage each other with a Patented July 25, l 967 varying degree of overlap during the expansion and contraction of working chambers separated by the vanes. In this fashion, the vanes are capable of withstanding higher pressures developed within the chambers without the size and shape limitations otherwise imposed by material strength requirements.

Another important object of the present invention is to provide an expansible chamber device of the aforementioned type wherein an arrangement of valve ports and passages in the housing, vanes and crankshafts control the supply and exhaust of fluid to the radially inner and outer chambers in order to facilitate cooling and pressure sealing of the chambers. High volumetric efliciencies may thereby be obtained in connection with fluid motors and pumps while extremely high compression ratios may be obtained in connection with internal combustion engines.

These together with other objects and advantages which will become subsequently apparent reside in the details of construction and operation as more fully hereinafter described and claimed, reference being had to the accompanying drawings forming a part hereof, wherein like numerals refer to like parts throughout.

Brief description 0 the drawing:

FIGURE 1 is a longitudinal sectional view through one form of expansible chamber device constructed in accordance with the present invention.

FIGURE 2 is an end elevational view of the device shown in FIGURE 1.

FIGURE 3 is a transverse sectional view taken substantially through a plane indicated by section line 33 in FIGURE 1.

FIGURE 4 is a transverse sectional view taken substantially through a plane indicated by section line 44 in FIGURE 1.

FIGURE 5 is a transverse sectional view taken substantially through .a plane indicated by section line 55 in FIGURE 1.

FIGURE 6 is a perspective view showing one of the rotor assemblies associated with the expansible chamber device.

FIGURE 7 diagrammatically illustrates various phases of the rotor assembly during one cycle of operation of the expansible chamber device.

FIGURE 8 is a partial longitudinal sectional view through another form of expansible chamber device constructed in accordance with the present invention.

FIGURE 9 is a transverse sectional view taken substantially through a plane indicated by section line 99 in FIGURE 8.

Description of the preferred embodiments Referring now to the drawings in detail, FIGURES 1-6 illustrate an expansible chamber device generally denoted by reference numeral 10, the basic components of which are mounted within a cylindrical housing generally referred to by reference numeral 12. In the form of the invention illustrated in FIGURE 1, the housing encloses two axially spaced compartments 14 and 16 between end walls 13 and 20. The compartments are separated by an intermediate partition wall 22 within which two sets of valve ports are formed similar to the valve ports formed in the end wall 20' and a bearing wall member 24. Thus, the compartment 14 is enclosed Within the annular housing portion 26 axially spacing the wall members 22 and 24 while the compartment 16 is enclosed within the annular housing portion 28 axially spacing the wall members 22 and 20. In the illustrated embodiment, the wall members 20' and 22 respectively mount along the longitudinal axis of the housing assembly 12, a pair of fuel injection nozzles 30 and 32 which project into the compartments. Extending into the housing assembly through the central bearing sleeve 34 of the end wall 18, is a power shaft 36. The inner end of the power shaft may be socketed within the wall member 24 which encloses a gear chamber 38 adjacent to the end wall 18. A plurality of pinion gears 40 are rotatably mounted Within the chamber 38 by the end wall mounted bearings 42 and mesh with a central gear member 44 connected to the power shaft 36. Accordingly, all of the pinion gears 40 are synchronized for rotation in the same direction in order to respectively rotate a plurality of rotor assemblies 46.

With continued reference to FIGURES 1 and 6, it will be observed that each rotor assembly includes crankshaft sections 48 and t} interconnected with a pinion gear 40' for rotation about the axis thereof. Connected to the crankshaft sections 48 and 50, are a pair of crankpins 52 and 54 disposed in 180 spaced relation to each other relative to the fixed axis common to the crankshaft sections 48 and 50 and the pinion gear 40. Also, the crankpins 52 and 54 are respectively disposed within the compartments 14 and 16. The crankpin 52 is interconnected between a pair of cylindrical valve'elements 56 and 58 respectively connected to the crankshaft sections 48 and 50 and journaled by bearings 60 within the wall members 24 and 22. Similarly, the crankpin 54 is connected between a pair of cylindrical valve elements 62 and 64 respectively journaled in the wall members 22 and 20. The valve elements 56, 58, 62 and 64 therefore provide spaced bearing support for the rotor assembly 46 about the rotational axis of the pinion gear 40. Further, each of the valve elements control the supply and exhaust of fluid to and from the compartments 14 and 16 through ports formed in the wall members 20, 22 and 24.

A similar arrangement of ports is provided in each of the wall members aforementioned relative to the valve element with which it cooperates. As shown in FIGURE 5 for example, each wall member rotatably mounts a plurality of rotor assemblies, six of such assemblies being shown in the illustrated embodiment with the rota tional axes of the rotor assemblies being circumferen tially spaced by equal amounts about the longitudinal axis of the housing. Thus, associated with each rotor assembly, are a pair of valve ports 66 and 68 through which fluid such as air is supplied or exhausted when the ports are registered with a valve passage 70 in an associated valve element. Fluid communication to and from the valve ports 66 and 68 in the case of the Wall members 22 and 24 may therefore be established by radial passages 72. In the illustrated embodiment, the valve ports 66 and 68 are formed as 40 sectors about the rotational axis of the associated rotor assembly. The valve ports 66 and 68 are also angularly spaced from each other from center to center by 100. The angular disposition of the ports for each rotor assembly is the same relative to the radial lines extending from the longitudinal center of the housing to the rotational axes about which the rotor assemblies are rotated.

The crankpins 52 and 54 of each rotor assembly, rotatably mounts about a movable eccentric axis, a camtype vane member 74 as more clearly seen in FIGURES 3, 4 and 6. Each vane member includes on opposite sides of the eccentric axis of the crankpin about which it is rotatable, asymmetrical Wedge portions 76 and 78 forming a planar sliding surface 80' extending between the two wedge portions and an angularly related planar sliding surface 82 intersecting the surface 80 at the wedge portion 76. Each of the wedge portions 78 is also provided with a transfer passage 84. The vane members as described are dimensioned in relation to the number of vane members and circumferential spacing between the rotor assemblies, so as to overlap by a varying amount in response to rotation of the rotor assemblies in synchronized relation to each other. Thus, as shown in FIGURES 3 and 4, the overlapping vane members enclose within each of the compartments 14 and 16, a radially inner chamber 86 and a radially outer chamber 88. In response to rotation of the rotor assemblies, the overlapping vane members through a camming action are constrained to angular movement about their respective crankpins because of the sliding contact between the planar surfaces and 82 of adjacent vane members causing the vane members to converge to limit positions shown in FIGURE 3 and diverge to limit positions shown in FIGURE 4. Thus, the inner and outer chambers 86 and 88 successively contract and expand opposite to each other. It will also be observed that in the limit positions shown in FIGURE 3, the vane members 74 overlap by a maximum amount through sliding engagement between the surfaces 80 and 82 along contact surface areas to enclose the inner chamber 86 by a partition wall of substantial thickness and strength throughout as compared to the partition Wall formed by the vane members when enclosing a maximum volume as shown in FIGURE 4. In the limit positions of the vane members shown in FIGURE 4, the vane members therefore overlap by a minimum amount while the transfer passages 84 are uncovered so as to establish fluid communication between the inner and outer chambers.

It will be apparent from the foregoing, that the rotor assemblies within each of the compartments 14 and 16 simultaneously undergo one cycle of operation during 360 rotation. Further, because of the 180 spacing between the crankpins ineach of the compartments 14 and 16, the operational cycles within the respective compartments will also be 180 apart in phase. Smoother cyclic operation of the expansible chamber device is thereby achieved while each of the rotor assemblies will be selfbalanced because of the 180 crank relationship between the crankpins thereof.

As diagrammatically illustrated in FIGURE 7, an operational cycle for the rotor assemblies relative to one of the compartments 14 and 16, begins with the crankpin in a zero degree position as shown at the end of an expansion phase with the volume of the inner chamber 86 maximum and the volume of the outer chamber minimum corresponding to that of FIGURE 4. In this phase position, the transfer passages 84 establish fluid communication between the inner and outer chambers. When the rotor assemblies undergo 30 rotation, the valve passages 70 are registered with the valve ports 66 and the transfer passages 84 closed. The inner chamber 86 is then being contracted to expel combustion products, in the case of an internal combustion engine, through the exhaust port 66 while the outer chamber is being expanded. Upon clos ing of the exhaust port 66 by continued rotation of the crankpins to the 60 phase shown in FIGURE 7, compression begins since the air then trapped within the inner chamber will be pressurized by continued contraction of the inner chamber. In the position of the crankpins, the expanding outer chamber 88 is supplied with fluid through the inlet port 68 then in registry with the valve passage 70. The inlet port closes after the outer chamber is charged when the crankpin reaches the position corresponding to FIGURE 3. In this phase posi: tion of the vane members, fuel ignition may occur because the radially inner chamber 86 is then contracted to its minimum volume and the fluid trapped therein compressed by a maximum amount. Thus, fuel may at this instant be injected through the nozzle 30 or 32. Power expansion of the inner chamber 86 will then ensue to complete a cycle when the crankpins return to the start positions uncovering the transfer passages 84 so that the charge of fluid within the outer chamber which was being compressed while the inner chamber expanded, may clean the inner chamber that subsequently opens to the exhaust port 66 at the beginning of the next cycle.

In view of the varying overlap between the vane members, they are better able to withstand the stresses produced as a result of the extremely high pressures resulting from combustion for example. Further, during expansion of the inner chamber, it is pressure sealed because the sliding surfaces 80 and 82 of the vane members are held in engagement with each other by the increasing pressure of the fluid compressed within the contracting outer chamber 88. Since the pressure within the radially inner chamber decreases as the inner chamber expands to its maximum volume, the outer chamber could be designed so that the pressure of the fluid therein will increase to a value causing a slight separation between the engaging surfaces 80 and 82 of the vane members at the end of the cycle or the beginning of the next cycle when fluid communication is established between the inner and outer chambers. This attribute of the expansible chamber device may be used to advantage in another form of the invention as shown in FIGURES 8 and 9. This embodiment of the invention may for example employ eight rotor assemblies 90 in an arrangement similar to that of FIGURES 1 through 6 except for the number of rotor assemblies and the configuration and dimensions of the vane members 92 associated with each of the rotor assemblies. Thus, in the limit positions of the vane members illustrated in FIGURE 9 enclosing an inner chamber 86' of maximum volume and an outer chamber 88 of minimum volume, a small gap 94 is formed between the planar engaging surfaces 96. Fluid communication is therefore established between the radially inner and outer chambers through the gaps 94 formed because of the increasing bias imposed on the vane members by the increasing pressure within the radially outer chamber 88 being opposed by a decreasing pressure in the expanding inner chamber 86'. Except for the manner in which fluid communication is established at the beginning of each cycle between the radially inner and outer chambers, operation of the expansible chamber device illustrated in FIGURES 8 and 9 is the same as that described in connection with FIGURES 1 through 7. It should of course be appreciated that other modifications and improvements may be made to enhance the operational reliability of the expansible chamber device such as the use of one way brake devices to limit rotation of the vane members in one direction about their respective crankpins should this be necessary. Also, the engaging ends of the vane members may be provided with sealing strips in order to eliminate vibration and metal fatigue.

The foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly all suitable modifications and equivalents may be resorted to, falling within the scope of the invention as claimed.

What is claimed as new is as follows:

1. An expansible chamber device comprising, a housing, a plurality of circumferentially spaced shafts rotatably mounted by the housing, a plurality of overlapping cam members having slidably engaging surfaces separating radially inner and outer chambers within said housing, means drivingly interconnecting said shafts for displacing said cam members to simultaneously expand and contract said chambers respectively between minimum and maximum volumes, and means .operatively mounting said cam members on the shafts for varying the area of said engaging surfaces in contact with each other during said expansion and contraction of the chambers.

2. The combination of claim 1 including valve means driven by said shafts for sealing one of said chambers during contraction thereof to pressure seal the other of the chambers during expansion thereof while the area of said engaging surfaces is decreasing.

3. The combination of claim 2 wherein said cam members are provided with ports uncovered by the engaging surfaces establishing fluid communication between the inner and outer chambers when the contact area of the engaging surfaces is at a minimum value.

4. The combination of claim 1 including valve means for effecting compression of fluid in one of said chambers during contraction thereof to momentarily separate said engaging surfaces as said one of the chambers approaches minimum volume and the contact area of the engaging surfaces decreases toward a minimum value.

5. An expansible chamber device having a plurality of drivingly interconnected crankpins rotatably mounting vane members forming radially inner and outer chambers, wherein the improvement comprises wedge portions on said vane members overlapping each other along contact surface by a varying amount in response to expansion and contraction of said chambers.

6. The combination of claim 5 including means for sealing the outer chamber during contraction thereof While the overlap between said wedge portions is decreasing.

7. An expansible chamber device comprising a housing having an annular wall and end walls enclosing a compartment, a plurality of axially extending vanes rotatably mounted in overlapping circumferentially spaced relation dividing said compartment into outer and inner oppositely varying working chambers, means mounting said vanes for rotation about relatively movable axes effecting successive expansion and. contraction of said working chambers, valve means for intaking fluid into said outer chamber and exhausting fluid from said inner chamber in timed relation to said expansion and contraction of the chambers, said vanes having wedge portion overlapping by varying amounts during said rotation of the vanes and means for transferring fluid compressed in the outer chamber to the inner chamber when the wedge portions of the vanes overlap by a minimum amount.

8. The combination of claim 7 wherein said mounting means includes a crankshaft for each of the vanes, a crankpin eccentrically connected to the crankshaft and rotatably mouting the vane about one of said relatively movable axes and gear means drivingly interconnecting said crankshafts.

9. The combination of claim 8 wherein said valve means comprises, a valve element driven by each of the crankshafts and intake and exhaust ports formed in the end walls registering with passages in the valve elements.

10. The combination of claim 9 wherein said fluid transferring means includes passage formed in the wedge portions uncovered when overlapping by said minimum amount to establish fluid communication between said chamber.

11. The combination of claim 7 wherein said fluid transferring means includes passages formed in the wedge portions when overlapping by said minimum amount to establish fluid communication between said chamber.

12. The combination of claim 7 wherein said fluid transferring means includes planar engaging surfaces on said overlapping wedge portions separated by a gap in response to pressure of fluid compressed in the outer chamber to establish fluid communication.

13. The combination of claim 12 wherein said mounting means includes a crankshaft for each of the vanes, a crankpin eccentrically connected to the crankshaft and rotatably mounting the vane about one of said relatively movable axes, and gear means drivingly interconnecting said crankshafts.

14. The combination of claim 13 wherein said valve means comprises, a valve element driven by each of the crankshafts and intake and exhaust port formed in the end Walls registering with passages in the valve elements.

(References on following page) References Cited UNITED STATES PATENTS Colbourne 9187 Homan 123-12 Cannizzaro 9189 Hopkins 103-126 8 2,410,341 10/1946 Delamere 103-117 3,207,425 9/1965 Morse 230141 FOREIGN PATENTS 483,929 4/1938 Great Britain.

DONLEY I. STOCKING, Primary Examiner. W. J. GOODLIN, Assistant Examiner. 

1. AN EXPANSIBLE CHAMBER DEVICE COMPRISING, A HOUSING, A PLURALITY OF CIRCUMFERENTIALLY SPACED SHAFTS ROTATABLY MOUNTED BY THE HOUSING, A PLURALITY OF OVERLAPPING CAM MEMBERS HAVING SLIDABLY ENGAGING SURFACES SEPARATING RADIALLY INNER AND OUTER CHAMBERS WITHIN SAID HOUSING, MEANS DRIVINGLY INTERCONNECTING SAID SHAFTS FOR DISPLACING SAID CAM MEMBERS TO SIMULTANEOUSLY EXPAND AND CONTRACT SAID CHAMBERS RESPECTIVELY BETWEEN MINIMUM AND MAXIMUM VOLUMES, AND MEANS OPERATIVELY MOUNTING SAID CAM MEMBERS ON THE SHAFTS FOR VARYING THE AREA OF SAID ENGAGING SURFACES IN CONTACT WITH EACH OTHER DURING SAID EXPANDING AND CONTRACTION OF THE CHAMBERS. 